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US4887580A - Supercharger device for reciprocating internal combustion engines, particularly for motor vehicles - Google Patents

Supercharger device for reciprocating internal combustion engines, particularly for motor vehicles Download PDF

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Publication number
US4887580A
US4887580A US07/173,525 US17352588A US4887580A US 4887580 A US4887580 A US 4887580A US 17352588 A US17352588 A US 17352588A US 4887580 A US4887580 A US 4887580A
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US
United States
Prior art keywords
rotor
supercharger
wedge
vanes
engine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US07/173,525
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English (en)
Inventor
Alfredo Hilfiker
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
PNEUMOFORE SpA A CORP OF ITALY
PNEUMOFORE SpA
Original Assignee
PNEUMOFORE SpA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from IT8767243A external-priority patent/IT1207546B/it
Priority claimed from IT8767773A external-priority patent/IT1211295B/it
Application filed by PNEUMOFORE SpA filed Critical PNEUMOFORE SpA
Assigned to PNEUMOFORE S.P.A., A CORP. OF ITALY reassignment PNEUMOFORE S.P.A., A CORP. OF ITALY ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: HILFIKER, ALFREDO
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Publication of US4887580A publication Critical patent/US4887580A/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/18—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber
    • F04C28/22—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/32—Engines with pumps other than of reciprocating-piston type
    • F02B33/34—Engines with pumps other than of reciprocating-piston type with rotary pumps
    • F02B33/36—Engines with pumps other than of reciprocating-piston type with rotary pumps of positive-displacement type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C18/3442—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the inlet and outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
    • F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into cylinder

Definitions

  • the present invention relates to a supercharger device for internal combustion engines, particularly for motor vehicles.
  • the employed power In the normal use of the motor vehicle, the employed power generally does not exceed 50% of the maximum power and this reduction, obtained by choking the induction, is matched by a decrease of the specific performance of the engine with consequent high consumptions, imperfect combustion and therefore presence of polluting products in the exhaust system.
  • the mechanical type used predominantly in small- and medium-cylinder capacity engines, draws the power required for supercharging from the driving shaft.
  • Superchargers of the "Roots" type are used which are driven by the engine with the interposition of a multiplier and of a joint which starts the supercharger only at a preset number of rpm of the engine.
  • the supercharging power is supplied by a turbine which is driven by the exhaust gases of the engine, and drives a feed supercharger.
  • the aim of the present invention is to provide a system for the controlled supercharging of reciprocating engines for motor vehicles, both of the "Otto" cycle type and of the "Diesel” cycle type, adapted to allow the abovesaid optimizing of power output with the consequent possibility of considerably reducing the cylinder capacities installed, achieving the peaks in required power by supercharging.
  • a supercharger device for internal combustion reciprocating engines comprising a positive displacement rotary supercharger inserted on the induction manifold of an engine, characterized in that said superchanger is constantly driven by the engine shaft, the capacity and therefore the delivery pressure of said supercharger being variable by virtue of a controlled variation of the geometry of pumping means of said supercharger, said pumping means comprising a stator cylinder, a rotor and vanes.
  • the geometry variation is obtained by varying, by virtue of the action of control elements, the eccentricity between the axis of the rotor and that of the stator.
  • the supercharger acts as a simple blower, and performs no supercharging action.
  • the supercharger performs its maximum supercharging, the degree whereof depends on the maximum compression ratio between the induction and the delivery of the supercharger and the number of rpm being considered.
  • the passage from one condition to the other is immediate and the response to the demand of power increase by supercharging is correspondingly immediate since there are no delays due to startup inertia.
  • the passage from one condition to the other can be performed at any rpm rate of the engine, so that supercharging, and the consequent power increase, can also be performed at low rpm.
  • the variation of the geometry of the pumping means is obtained by means of elements adapted to produce, upon the action of external control means, the retention of the vanes in the respective seats of the rotor.
  • the passage from aspirated operation to supercharged operation of the engine therefore occurs by acting on said control elements to produce the retention or respectively the release of the vanes.
  • FIG. 1 is a schematic view of the system according to an embodiment of the present invention, wherein the geometry variation of the pumping means is obtained by varying the eccentricity between rotor and stator; the system being illustrated in the engine supercharging condition,
  • FIG. 2 is a similar schematic view illustrating the system at rest in conditions of non-supercharged operation of the engine
  • FIG. 3 is a diagram related to the engine of FIG. 1,
  • FIG. 4 is a sectional view of the supercharger taken along the line IV--IV of FIG. 1,
  • FIG. 5 is a sectional view, similar to the previous one, illustrating a supercharger according to a variated aspect of the invention
  • FIG. 6 is a schematic view, similar to FIG. 1, illustrating another embodiment of the present invention in which the geometry variation of the pumping means is obtained by retention of the vanes,
  • FIG. 7 is a transverse sectional view of a supercharger with pneumatic means for the retention of the vanes according to FIG. 6,
  • FIG. 8 is an axial sectional view of the rotor taken along the line VIII--VIII of FIG. 7,
  • FIG. 9 is a sectional view, similar to FIG. 7, illustrating a supercharger with mechanical vane retention means, according to a further aspect of the invention.
  • FIG. 10 is a sectional view taken along the line X--X of FIG. 9,
  • FIG. 11 is a partial sectional view, in enlarged scale, of a rotor, with mechanical retention means, according to another aspect of the invention.
  • the letter M generally indicates an internal-combustion reciprocating engine, for example an "Otto" cycle engine, of the carburation type provided with an induction manifold 10 whereon is inserted a choke carburettor 11.
  • a positive-displacement rotary supercharger 13 of the known type comprising a stator 14 and an eccentric rotor 15 bearing a plurality of vanes 115, freely slideable in respective seats 116 of the rotor.
  • the assembly constituted by the stator, by the rotor and by the vanes is briefly defined as pumping means.
  • the geometry of the pumping means is variable, and in the illustrated example this is obtained by varying the eccentricity between the stator cylinder 14 and the rotor 15, by means of control elements 16, from zero to a maximum value which depends on the difference between the diameters of the stator and of the rotor.
  • the stator 14 is oscillably suspended from a pivoting pin 17 about which it can rotate to move with respect to the rotor 15, which is fixed, to pass from the maximum-eccentricity configuration illustrated in FIG. 1 to that of zero eccentricity illustrated in FIG. 2.
  • the control elements 16 may be of different types, for example they can be constituted by a hydraulic piston 18 acting in contrast with a spring 19, or they can be mechanical and either direct or power-assisted.
  • the supercharger produces the maximum volumetric capacity and the maximum pressure, providing the maximum supercharging of the engine M at the number of rpm being considered.
  • the volumetric capacity of the supercharger is in fact related to the number of rpm by the following relationship ##EQU1## where D is the inner diameter of the cylinder 14, d is the outer diameter of the rotor 15, L is the axial length of the supercharger, n is the number of rpm being considered and ⁇ .sub. ⁇ is the volumetric efficiency.
  • This supercharging corresponds to a variation in the power W as illustrated in the diagram of FIG. 3 wherein the insertion of the supercharging by shifting the cylinder 14 of the supercharger with respect to the rotor 15 occurs, for example, at 3500 rpm.
  • the broken-line curve W relates to the power of the engine M operating at atmospheric pressure
  • the curve W relates to the power of the same engine supercharged by the supercharger 13
  • the solid connecting line between the two curves represents the power variation as a consequence of the insertion of the supercharger.
  • the maximum power variation is closely related to the volumetric compression ratio of the supercharger 13 and for a value of 1/1.5 of said ratio it can be estimated, other conditions being equal, between 25% and 35% of the maximum power developed by the engine M with aspirated operation.
  • the engine M with the supercharging system according to the invention may be advantageously fitted to motor vehicles requiring engines with approximately 20-30% higher power, since, in case of need, the power demand is met by inserting the supercharger 13 in the specified manner.
  • the supercharger performs a simple ventilating effect, with a considerable increase in turbulence; the volumetric flow rate of the airflow supplied thereby, substantially at atmospheric pressure, being expressed by the following relation: ##EQU2## where the symbols have the previously specified meanings.
  • the load on the supercharger is minimal and there is no relative movement of the vanes with respect to the recesses of the rotor, this in practice eliminating the need for adequate lubrication.
  • FIG. 4 illustrates an advantageous constructive embodiment of the supercharger 13.
  • a plate 30 has a seat 31 for supporting the shaft 32 of the rotor 15.
  • the plate 30 has a perfectly planar surface 33 facing towards the stator cylinder 14 which is oscillably supported by an arm 34 articulated to the pivot 17 rigidly associated with the plate 30.
  • a series of elastic washers 35 engaged by a locking nut 36, keeps the stator cylinder 14 in sealing contact engagement against the surface of the plate 30; the seal being ensured by an "O"-type gasket accommodated in a front recess of the cylinder.
  • the shaft 32 of the rotor 15 is supported by a first bearing and by a second bearing, respectively 37 and 38.
  • FIG. 5 shows a superchanger, according to a further aspect of the invention and which differs from the one previously described in that the stator cylinder is flanged directly onto the plate 30 having a through seat 43 which is circular but eccentric with respect to the cylinder 14 wherein a bush 44 is accommodated, freely rotatable, and is eccentrically provided with the bearing 37 for supporting the shaft 32.
  • the eccentricity of the bush 44, with respect to the cylinder 14, is identical to that of the shaft 32 with respect to the bush, so that, by rotating through 180° the bush 44 is the seat of the plate 30, the two eccentricities compensate one another and the rotor 15 arranges itself coaxial to the cylinder 14.
  • a pivot 45 is provided on the bush 44 to allow the connection of a tensioning element 46 adapted to produce the rotation of said bush in its seat.
  • FIGS. 6-11 show a supercharger, according to another aspect of the invention, in which the variation of the geometry of the pumping means is obtained by subjecting the vanes 115 of the rotor to elements adapted to produce, upon the action of an external control K, the retention of said vanes in the respective seats 116 of the rotor.
  • the rotor is provided with elements for retention by negative pressure, comprising an axial channel 214 connectable to a negative pressure source and a plurality of derived channels 215, axially spaced (FIG. 8), adapted to subject the vanes 115 to said negative pressure to keep then fully inserted in their seats 116.
  • the negative pressure source may be constituted by the induction manifold 10 of the engine M which is connected to, or disconnected from, the duct 214 by means of the valve K constituting the external control. If required, the action of the induction manifold may be integrated with an accumulation container R and/or with an auxiliary negative pressure source, for example constituted by an ejector associated with the exhaust manifold and also by temporarily using the supercharger as vacuum pump.
  • Each of the derived channels 215 ends with a widened aspiration inlet 216 which faces the lateral wall of the respective vane seat 115.
  • each vane as an effect of the negative pressure, is aspirated and drawn in forced contact engagement against said wall of its seat and, by virtue of the friction, is retained inside said seat after it has been pushed therein by the contact with the stator as an effect of the rotation of the rotor.
  • auxiliary derived channels 217 which lead onto the dead bottom of the seats 115 and act by direct aspiration on the related vane.
  • the channels 217 are in any case indispensable to ensure the correct operation of the supercharger at high rpm in view of the need to rapidly evacuate the air which is on the bottom of the vane seat.
  • the vanes 115 are subject to the action of mechanical retention elements constituted by cylindrical cams 230 rotatably contained in corresponding cylindrical seats 231 communicating with the seats 116 and retained therein by retention screws 225.
  • the small shaft 235 is subject to a control, coherent with the type of the sets of teeth 233-234 which may be mechanical or fluidodynamic and the actuation whereof moves the cams 230 angularly to engage or disengage their active surfaces 232 with or from the lateral face of the related vane 115.
  • the cylindrical cams are replaced by wedge-shaped radial blocks 240 slideable in corresponding wedge-shaped radial seats 241 provided on the rotor 15. As visible in FIG. 11 the wedge-receiving radial seats 241 taper in the centrifugal direction of the seat.
  • the blocks 240 have a wedge-shaped surface 242 intended to make contact with the lateral surface 115a of the corresponding vane 115 through a slot 243 which connects the seats 116 and 241.
  • Each block 240 is subject to the action of the centrifugal force which pushes the wedge-shaped surface 242 against the lateral surface of the vane 115 to retain the vane and is provided with a threaded hole 245 in which the correspondingly threaded portion 246 of a return shaft 247 engages.
  • the other end of the shaft 247, opposite to the threaded portion 246, has a pinion 248 engaging with the toothed portion 234 of the control shaft 235 described with reference to the previous FIG. 9. It is obvious that the rotation of the shaft 235 causes a radial movement of the wedge-shaped block 240 which, depending on the direction of rotation imparted to the shaft, moves, pushed by the centrifugal force, to engage the vane 115 or, against the action of said force, to disengage it; the control being extremely gradual, to the advantage of a controlled release of the vanes.
  • the supercharger as illustrated in FIGS. 6 to 11 substantially has the following advantages:
  • the rotor, the eccentricity whereof with respect to the stator is fixed and constant may be supported at both ends and therefore is not subject to limitations in axial extension with the consequence that, with equal delivered power, the diameter can be reduced and the peripheral speed of the vanes during supercharging can be reduced accordingly;
  • the rotor of the supercharger may be used as dynamic balancing shaft of the engine or at least as integrating element of said shaft.
  • the rotor is keyed, directly or by transmission means such as gears, or chains, or toothed belts 260, and, besides having a compact configuration, allows to angularly time the rotor and the shaft of the engine to synchronize the pressure waves caused by each vane with the filling phase of each cylinder, thus increasing the degree of filling of the cylinder, especially at low rpm, as an effect of the additional dynamic pressure.
  • the rotor 10 is counter-rotating with respect to the driving shaft and can therefore be sized and counterweighted so as to also perform the function of dynamic balancing shaft.
  • the rotor of the supercharger if counterrotating and at equal rpm with the engine, can balance the inertial forces due to the first-order harmonics.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)
  • Rotary Pumps (AREA)
US07/173,525 1987-03-30 1988-03-22 Supercharger device for reciprocating internal combustion engines, particularly for motor vehicles Expired - Fee Related US4887580A (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
IT8767243A IT1207546B (it) 1987-03-30 1987-03-30 Particolarmente per autoveicoli sistema per la sovralimentazione transitoria controllata di motori alternativi a combustione interna
IT67243A/87 1987-03-30
IT67773A/87 1987-09-11
IT8767773A IT1211295B (it) 1987-09-11 1987-09-11 Perfezionamento ai sistemi per la sovralimentazione transitoria controllata di motori alternativi acombustione interna per autoveicoli

Publications (1)

Publication Number Publication Date
US4887580A true US4887580A (en) 1989-12-19

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
US07/173,525 Expired - Fee Related US4887580A (en) 1987-03-30 1988-03-22 Supercharger device for reciprocating internal combustion engines, particularly for motor vehicles

Country Status (6)

Country Link
US (1) US4887580A (pt)
EP (1) EP0288738B1 (pt)
JP (1) JPS63302129A (pt)
BR (1) BR8801489A (pt)
DE (1) DE3861739D1 (pt)
ES (1) ES2021404B3 (pt)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5246064A (en) * 1986-07-29 1993-09-21 Showa Aluminum Corporation Condenser for use in a car cooling system
US5368004A (en) * 1994-02-15 1994-11-29 Mann; Leslie Automobile supercharger utilizing flywheel
US5482112A (en) * 1986-07-29 1996-01-09 Showa Aluminum Kabushiki Kaisha Condenser
US6434939B1 (en) * 2001-02-21 2002-08-20 John Herbert Beveridge Rotary piston charger
US20060120895A1 (en) * 2004-11-26 2006-06-08 Gardner Edmond J Rotary positive displacement engine
CN101943067A (zh) * 2009-07-01 2011-01-12 罗伯特.博世有限公司 运行内燃机的方法

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2524257B2 (ja) * 1990-11-06 1996-08-14 本田技研工業株式会社 内燃機関における過給圧制御方法
IT1403001B1 (it) * 2010-11-29 2013-09-27 Vhit Spa Pompa per vuoto, in particolare per autoveicoli.

Citations (6)

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CH105394A (de) * 1922-12-13 1924-09-01 Gruebler Felix Verbrennungsmotor mit konstantem Verdichtungsdruck in wechselnden Höhenlagen.
US2696790A (en) * 1951-10-23 1954-12-14 Amos E Crow Variable discharge pump
US4472119A (en) * 1983-06-30 1984-09-18 Borg-Warner Corporation Capacity control for rotary compressor
US4516919A (en) * 1983-06-30 1985-05-14 Borg-Warner Corporation Capacity control of rotary vane apparatus
JPS60209629A (ja) * 1984-04-02 1985-10-22 Jidosha Kiki Co Ltd 過給機付内燃機関
JPS6223530A (ja) * 1985-07-24 1987-01-31 Isuzu Motors Ltd 過給装置

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FR1058139A (fr) * 1951-08-23 1954-03-15 Teves Kg Alfred Pompe ou moteur à réglage automatique pour fluides liquides ou gazeux sous pression à remplissage intégral sans tiroir distributeur
FR2076385A5 (fr) * 1970-01-13 1971-10-15 Trw Inc Pompe centrifuge
DE2035355A1 (de) * 1970-07-13 1972-02-17 Maschinenfabrik Karl Wittig Gmbh, 7860 Schopfheim Drehschieberverdichter
DE2928169A1 (de) * 1979-07-12 1981-01-29 Wilhelm Jakobi Fluegelzellen-rotormaschine
DE3144712C2 (de) * 1981-11-11 1984-11-29 Pierburg Gmbh & Co Kg, 4040 Neuss Verfahren zur Regelung der Füllung von Brennkraftmaschinen mit Verbrennungsgas sowie Vorrichtung zum Durchführen dieses Verfahrens
AU1486483A (en) * 1982-05-31 1983-12-08 Commonwealth Of Australia, The Power source

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH105394A (de) * 1922-12-13 1924-09-01 Gruebler Felix Verbrennungsmotor mit konstantem Verdichtungsdruck in wechselnden Höhenlagen.
US2696790A (en) * 1951-10-23 1954-12-14 Amos E Crow Variable discharge pump
US4472119A (en) * 1983-06-30 1984-09-18 Borg-Warner Corporation Capacity control for rotary compressor
US4516919A (en) * 1983-06-30 1985-05-14 Borg-Warner Corporation Capacity control of rotary vane apparatus
JPS60209629A (ja) * 1984-04-02 1985-10-22 Jidosha Kiki Co Ltd 過給機付内燃機関
JPS6223530A (ja) * 1985-07-24 1987-01-31 Isuzu Motors Ltd 過給装置

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5246064A (en) * 1986-07-29 1993-09-21 Showa Aluminum Corporation Condenser for use in a car cooling system
US5482112A (en) * 1986-07-29 1996-01-09 Showa Aluminum Kabushiki Kaisha Condenser
US5368004A (en) * 1994-02-15 1994-11-29 Mann; Leslie Automobile supercharger utilizing flywheel
US6434939B1 (en) * 2001-02-21 2002-08-20 John Herbert Beveridge Rotary piston charger
US20060120895A1 (en) * 2004-11-26 2006-06-08 Gardner Edmond J Rotary positive displacement engine
CN101943067A (zh) * 2009-07-01 2011-01-12 罗伯特.博世有限公司 运行内燃机的方法
CN101943067B (zh) * 2009-07-01 2015-07-01 罗伯特.博世有限公司 运行内燃机的方法

Also Published As

Publication number Publication date
EP0288738A1 (en) 1988-11-02
BR8801489A (pt) 1988-11-08
JPS63302129A (ja) 1988-12-09
ES2021404B3 (es) 1991-11-01
DE3861739D1 (de) 1991-03-14
EP0288738B1 (en) 1991-02-06

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Owner name: PNEUMOFORE S.P.A., VIA SAGRA S. MICHELE 66 -10100

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